Motion tfjinslttlttting device



Sept. 6, 1932. Y J.' H. WILLIAMS MOTION TRANSMITTING DEVICE s sheets-sheet i Filed April 2l, 1951 ArrOR/vfys sept. s, 1932.

J. H. WILLIAMS 1,875,537

MOTION TRANSMITTING DEVICE Filed April 2l. 1951 5 Sheets-Sheet 3 Array/w96.

Patented Sept. 6, 1932 omni-:io .sr-11A res orf-nce 'JAMES 'non/'Anp WILLIAMS, .on TRovnnnon, RHODE ISLAND, AssIGNon .To `Innrnorr '-rn'nsr ooivirnNY, er D'erlnon MIonisAN, A 'conne-Remon QFMICHIGAN 'MTION TBANSMITTING DEVICE A'ppneatipn `fue.: prrr-21,

The present invention relates'to a 'motion transn'iitting ydevice for obtaining simult'a- A neeus, frelative, rectilinear and @rotational inet/erneutebetween a'to'ol andthe vvoilrupon I, Whicliet operates and `forlnaintaining apre- 0 Y I determined ratio between their speeds of relative linear movementnndtheir speeds'of rel e tive angular movement.

In various-machines, particularly those forv Te linear movement during the -simultan eue relative reciprocating and oscillating inoyements. The 'correlated yrotational and linear movements above referred lto Eare inl in machines -in ywhich the 'tool is ed to' automatically follow @the con-tour t tootliiaces either along -involutes-or helices thereof. -In'machineslsuch as'abve e "red to, AWhere(the tool and the Worlrl are air-.calin correct eng-agement Whilethey li eereiative rotati onal and rectilinear move-4 y l the ratio between the-ratesofrectiisear rotational movement -is detern iefil in 'each 'case by the particular,gear J which is'to be eut orinished by the machine and' when it is desiredft'o set up the machine for operation on-"a gearhavingadifferent torm.- a diierent speedl ratio suitable :torithe gearto be acted upon must-be provided.

Various terms- 'of motion l transmitting devices suchvv as, gear trains7 cams, tapes, helicalY tive rotational movement andthe speeds .of

capable of maintainingonlyar single prebe operated upon to remove =the motion transmitting device and Vreplace -it with an other capable of maintaining the desired speed ratio. Where -a single machine is requiredto operate upongears which differin size, Vhelix angle and other characteristics, itis necessary'to hav'cfonhandfa largefnumber of 4rather expensive `replacement parts and considerable'time fis lost in adj ustingithe machine "for different jobs.

providea motionf transmitting deviceifor 'cor-` The presentinvention has for its objectto .60

relating :li-near `and rotational movements Which Iis ac ljustalole in fsuchf a' lmanner as to obtain` any desired lratio between :the-'speeds of angular and linear 'movements lWithin relatively -Wide limits.

A further object is to providefa `motion transmitting device controlledxby a single rotatably mounted :member `Whichgis accurately graduated Vto indicatethe angular adjustments :thereof y'and which `serves lto maintain a fix-eclratio :between the speeds 0f relative linear -and angular vvmovements :of

the tool and Work which is a function of the anglev of adjustment ofthe controllingrmember.

With'the i -abovefa'nd other obj e'cts fin rr'fiew,` i

the invention may 'be said 'to comprise the motion l'transmitting device :as illustrated in the accompanying drawings, hereinafter described and'particularlyset forth in'thezappended claims; together Withy such variations and modifications thereof Tas will be' app arent toone skilled inthe-'fartto Whichfv'the inventionappertains. y f,

Reference shouldv be had'to` the accompanying drawings-forming apart ofthis specification, in which: l Fig. f1 isa vertical cross sectiongofia gear lapping machine to .which the invention-is. applied, the section j being -taken fon the line` indicated-at 1-.1 ofFig. f4; kg

Fig..2is a sectiontaken"onfthe'line indicated at Q-Qin Fig. l;` l

8 is la Asection taken, on 'the `line .indicated at B-B'in-Fig. l; A A 4 A 1 Fig. i isy a -front elevation ofthe machine. partly in section as 4indicated by `the line 4 4 1n l; Y

Fig, is a vertical section taken on the line indicated at 5-5 in Fig. 1;

Fig. 6 is a vertical section through the motion transmitting device for oscillating the reciprocating lap with a speed of angular movement proportional to the speed of linear movement, the section being taken on the line indicated at 6-6 in Fig. 8, showing the actuating guide set in vertical position;

Fig. 7 is a vertical section taken in the plane indicated by the line 8-8 in Fig. 6 but showing the actuating guide disposed at an angle to the vertical;

Fig. 8 is a section taken on the'line indicated at 8 8 in Fig. 6

v Fig. 9 is a section taken on the line indi-V cated at 9-9 in Fig. 6; v

YThe device of the present'i'nvention is applicable generally to machines in which a work holder and tool are required to have co-related relative, reciprocating and oscillating movements in which a predetermined ratio is maintained between the linear and angular speeds, and is herein illustrated as applied to a gear lapping machine of the type disclosed in the patent to Copeland et al No. 1,683,868, granted September 11, 1928. The device of the present invention is employed in machines of the type vreferredto for imparting oscillatory movements to the reciprocating lap carrying spindle, and for maintaining a predetermined ratio at all times between the speed of linear movement of the spindle and the speed of angular movement thereof, to maintain an invariable engagement between lap tooth faces and gear tooth faces during axial reciprocation of the lap, the lap and gear having the form of complement-al internal and external helical gears.

As shown in Fig. lief the drawings, the

. machine is provided with a lap 1 which has the form of an elongated internal gear of a form complemental to that of a gear 2 to be finished. The gear 2 is positioned in axial l alignment with the lap 1 and is adapted to telescopically engage with the lap 1 during relative axial reciprocation of the gear Vand lap. A stream of-liquid carrying fine abrasive particles is caused to flow over the gear and through the lap so that abrasive particles -are caused to enter between opposed faces of the teeth of the gear and lap so that the tooth faces of the gear which press against tooth faces of the lap during the reciprocation are abraded, and slight discrepancies in the contour of the lap and gear tooth faces areworn down until the gear tooth faces are engaged by the lap tooth facesthroughout substantially their entire areal This lapping operation serves toY eliminate slight errors in the teeth of thegears especially those which are introduced in the hardening heat treatment to which the gears are subjected after they are cut.

The gear 2 is rigidly held by means of clamping plates 3 and 4 on an arbor 5 which is clamped between upper and lower centers 6 and 7 at the lower and upper ends, respectively, of upper and lower clamping spindles 8 and 9. The lower spindle 9 is rigidly supported at its lower end in a bracket 10 fixed to the frame 11 of the machine, and the spindle 8 is mounted withina sleeve 12 which is slidably mounted inthe upper portion of the frame 11. The arbor 5 is xed to the lower end of the sleeve 12 by means of a suitable chuck 13 and the sleeve 12 may be adjusted vertically to exertan axial clamping thrust on the arbor 5 by means of a hand wheel 14 which is connected by means of a shaft 15 with a pinion 16 which meshes with a gear nut 17 which has threaded engagement with a threaded section 18 of the sleeve 12. The section 18 is attached to the sleeve 12 by suitable means which holds the sleeve 12 against axial movement with respect to the section 18 but which permits the sleeve 12 to turn within the threaded sleeve 18 which is held against rotation in the frame 11. Rotation of the nut 17 causes the sleeve 12 and spindle 8 to be raised or lowered to clamp or release the arbor 5 which is rigidly held against endwise movement during operation of the machine.

The lap 1 is carried by the upper end of a tubular spindle 19 which is concentrically mounted with respect to the lower fixed spindle 9 and through which the spindle 9 extends. The spindle 19 is rotatably supported in ball bearings 2O and 21 in a housing 22 which is slidably mounted on the frame 11 for vertical movement. rlhe housing 22 is held against turning movement and is guided vertically by means of guide posts 23 positioned at opposite sides of the spindle 19 and rigidly secured to the frame 11.

In the operation of the machine the lap 1, spindle 19 and housing 22 are reciprocated bodily as a unit to cause the lap 1 to act upon the gear 2 which is in telescopic engagement with the lap during reciprocation of the lap. Vertical reciprocation is imparted to t ie housing 22, tubular spindle 19 and lap 1 by means of an actuating lever 24 which has a forked forward end 25 pivotally attached to the bottom of the housing 22 on opposite sides of the spindle 19. The lever 24 is pivoted at its rear end to the upper end of the short link 26 which is pivoted Vat its lower end to a bracket 27, fixed to the rear side of the frame 11. |The lever 24 is oscillated vertically by means of an actuating link 28 which is suspended from a crank arm 29 on a crankshaft 30 and pivoted at its lower end to the lever 24 intermediate the ends thereof. As the crankshaft 30-is rotated the lever 24 is oscillated vertically and its forward end is raised and lowered causing the housing 22 attached thereto to reciprocate vertically. During oscillation ofthe lever 24, 'the` short linkv 26 rocks about its pivot to permit the forward end of the lever which is attached to the housing to move vertically in a straight line. The crankshaft 3) has rfixed thereto a gear 3l. which meshes with a gear 32 which is rotatahly mounted on ar counter shaft 33 and which is adapted tofbe connected to the shaft 33 for rotation therewith by means of a suitable clutch34.. The shaft 33 has a suitable driving pulley 35 fixed thereto which may ybe driven from any suitable source of power.

The crankshaft 30 may also beprovided with a suitable brakeV 36 which may be operated toA stop the machine in the `desired position after the clutch 34 is released, and thecranlr- `shaft may also be provided with a suitable e load equalizing spring 37 which acts to coun- .terbalance the weight of the housing, lap and sleeve whose weight is imposed upon -the cuter end of the lever 24, the spring 37 being stretched during the downward movement of the lever 24 and acting to assist in the elevation of the housing and lap during the upward movement of the lever 24.

Means may be provided for automatically indexing the gear 2 with respect to the lap- 1 at predetermined intervals and at the ends on the face of, a wheel 45A and causing themf to enter the spiral groove. The pins 44 are at equal radial distances from the axis of the wheel 45 and are equiangularly spaced, the spacing of the pins 44'being suoli that one pin may closely: overliethe top` face of the wheel V41 while another is positioned contiguous to the bottom facey of said wheel. .During each revolutionof the index wheel 41 the pin 44 in engagement with the underside of the wheel 41 is engaged hy theprojecting lip or scoop 43 and is caused to enter the groove 42 and move upwardly until it clears the wheel, each revolution of the wheel 41 serving to turn the wheel 45 through an angle corresponding to the angular spacing of `the pins44 thereon.

The wheel 45 is fixed to a shaft 46 which carries a gear 47 meshing .with a gear 48 on i l55 thereon meshing with` a worm gear 56 splined to the sleeve Change gear 51 may have the same number of teeth as the gear being lapped and the other gears in the train connecting the index wheel and the sleeve 12 .may be so proportioned that the sleeve l2 and gear 2 attached thereto will be turned through an angle lcorresponding to the angular spacing of the teeth of the gear 2 upon each revolution yof the index wheel, as VWell understood in the art.

As shown in Fig. 2 of the drawings, shaft .49 may drive a sprocket chain 57 actuating mechanism indicatedgenerally at 5 8 for automatically stopping the machine after a predetermined number of revohit-ions.` This mechanisni, however, does not' concern, the present invention and vis not described in detail.

When the gear to be lapped is in the form of a helical gear the lap must he in the form of an internal helical gear coinplemental lto vthe gear to be lapped, and in order to permit the gear to pass axially through the lapit is necessary for either the (rear or lap to have a turningiinovement as the gear is'moving axially through the lap, and in order tomake it possible to accurately control the abrasive action, itis desirable that this turni-ng movement be imparted to the gear or lap independently of the thrust of the interengaging teeth of the `gear and ylap by a positive actuating mechanism, so'that there will be no variation in the relative positions of opposed tooth faces during the reciprocating stroke. In other Words, the ahrading surfaces of the lap teeth should 1be constrained by the actuating mechanism to move along the helices of the gear tooth faces, and in order to accomplish this result it is necessary that the actuating mechanism impart to the lap or'goar an angular movement at a speed proportional to the speed of relative axial movement between the gear and lap, If, as herein'illustrated, the lap be oscillated ahoutitsaxis during itsre- -cipro'cation, the rate. of turning movement must at all times be at a predetermined ratio to the rate of relative axial movement so that each point on the lap tooth surfaces will trace a helix about the common axis of the gear and lap corresponding to thc helices of the gear `tooth faces at corresponding distances from the common axis. For instance, if the helix angle of the gear measured on its pitch cylinder is 45 degrees, the angular speed of the lapat any instant measured on the pitch cylinder must be equal to itsspeed of axial movement relative to the gear. For vother helix angles the rate of angularmovement measured on the pitch cylinderr equals the rate of relative axial movement times the tanpgent of the'helix angle, the rate of angular movement being .Zero for spurgears, which have a zero helix angle,andr graduallyfiiicreasing for gears and laps of progressively greater helix angles, Y i n Various relatively simple" mechz'mmcalV devices have been employed for imparting angular movements proportional to the linear movement of a reciprocating element, either to the reciprocating element itself or Ato a cooperating element of the machine, such as interposed trains of -gearing helical guides, cams, tapes and the like. Such devices are in general capable of maintaining only one predetermined ratio between the rate of linear and angular movement and are employed in the form of detaehably mounted interchangeable parts which must be replaced in setting up the machine for operation on a gear dierent from gears previously operated on.

Variations in helix angles, pressure angles, diameters and other controlling characteristics of gears are infinite in number, and customers often demand gears which differ from common standards with respect to one or more of these characteristics. This may make it necessary for the gear manufacturer to make special controlling parts to enable his machines to produce the gears required.

The present invention provides a motion transmitting device which is capable of minute adjustmentsy in order to obtain any desired ratio between linear andV angular movements which may be required so that the machine may operate upon any gear within the capacity of the machine without interchanging any of the parts of the motion transmitting mechanism.

As illustrated herein, the motion transmit- '.'f ting mechanism is contained within the housing 22 and acts to impart to the lap carrying spindle 19 an angular movement proportional to the rate of linear movement thereof.

As shown in Figs. 1, 3 and 4, a pair of laterally spaced vertical posts 59 are attached to the bracket adjacent its outer end and extend upwardly through the housing 22, which ris provided with bushings 22a slidably engaging the posts 59. The upper ends of the guide posts 59 are enclosed in sleeves 60 attached to the top of the housing 22 and the upper end of these sleeves are closed by caps 61. The sleeves and caps 61 provide air chambers above the upper ends of the posts 59 into which air willpass from the interior of the housing 22 through the restricted space between the posts 59 and sleeveGO during the upward movement so that an air cushion is provided which assists the spring 37 in 1 equalizing the load onthe crank shaft during reciprocation of the housing 22 and the7 lap spindle carried thereby.

The supporting posts 59 provide affixed 'support for a supporting drum62 which maj1 be in the form of a casting having integral bearing brackets 63 which are slidably received on the posts 59 and which may be held in desired position of vertical adjustment on the posts by means of set screws 64. The posts 59 are positioned forwardly of the spindle 19 and the' supporting drum 62' which is disposed centrally with respect to the housing and tubular spindle 19, is positioned between the supporting posts 59 and the spindle 19. At is inner end the drum 62 has an outwardly projecting circular flange 65 upon which a supportingannulus 66 may be mounted for angular adjustment about a horizontal axis, the annulus 66 being clamped upon the shouldered periphery of the flange 65 by means of a flat clamping ring 67 which is secured to the rear face of the annulus 66 by means of bolts 68 to clamp the annulus 66 in adj usted position on the flange 65. The annulus 66 has a guideway extending diametrically across the inner face thereof and disposed in a vertical plane which is formed by parallel guide bars 69 rigidly attached to the face of the annulus. A slide 70 isv received between the pair of parallel guide bars 69 and this slide is pivotally mounted upon a short horizontal shaft- 71 which is aliixed at its inner end to a slide 72 which is guided for horizontal movement between guide bars 7 3 attached to the inner face of the rear wall of the housing 22 by means of bolts 74h rhe short shaft 71 has a head 75 at its inner end which engages in a recess on the inner side of the slide 72 and, forwardly of the slide 72, the shaft 71 carries a bushing 76 which is clamped against the rear face of the slide 72 by a washer 77 and a nut 7 8 on the forward end of the shaft 71. rllhe bushing 76 lits in the central opening of the slide 7 O which iS held between the inner ends of the bushing 7 6 and the washer 7 7 with sui'cient play to permit the slide 70 to turn freely onthe bushing 76. lt will `be apparent that the slide 72 which is held between the horizontal guides 73 is constrained to move vertically with the housing 22 and is free to move horizontally in the guide 'during such vertical movement. n

By adjusting the supporting annulus 66 angularly the bars 69 forming a guideway for the slide 7 0 may be disposed at an angle to the vertical and, when the annulus is so adjusted it will be apparent that slide 72 must move horizontally during the vertical movement of the housing. It will further be apparent that the rate of horizontal movement of the slide 72 will always be proportional te the rate of vertical movement of the housing, the measure of the rate of horizontal movement being the rate of vertical movement times the tangent of the angle of the fixed guideway with respect to the vertical. The annulus 66 may be adjusted to dispose the guideway on the inner face thereof at any desired angle with respect to the vertical and it will, therefore, be apparent that any desired ratio maybe obtained between the rates of the vertical and horizontal movements imparted to thev slide 72. The movably connected slides 70 and 72 provide a loatinghead interposed'between thefhousing` and the relatively fixed.- supportfwithin thehousing which moves in' the directionl of movement ofthe housing and may also move `in allateral direction, the rates of movement of the slides in vtheir guidewaysbeing at a fixed ratio'to the rate of movement of the connectionl with one of the slides of the float;

ing head above described, it is apparent that the-ratio between the rate of angular movement ofthe rotatable member and the rate loi linear movement of the housing may be varied in iine graduations by adjusting the angula'rityv of the iixed guideway.

In themachine herein illustrated the slide 72 is mounted to travel at right angles tothe spindle 19 and is employed to transmit a rotary movement to lthe spindle 19'. Any suitable motiony transmitting' means capable of converting uniform rectilinear motion into uniform rotary motion may be interposed be'- tvveenl the slide 7 2 and the tubular spindle 19 such as a rack bar 7 9 attached to the inner pinion l fixed to the tubular spindle 19. l

As best shown in Figs. 7 and 8, graduations `81 are provided along the margin of the outer face of the ii'ange 65 and graduations 82 are provided on the outer faceI of the clamping ring 67 along the inner margin thereof to registerwith the graduations' 81 on the fiange..

As herein shown, the graduations are in degrees and serve to indicate the angular position of the guidevvay formed by the guide bars 69. In Fig. 7 of the drawings,the

guideway is shown disposed at an angle' of Y twenty degrees to the vertical, andin Fig. 8

the guideway is shown vdisposed in vertical' position. When the guidevvay isY disposed in vertical position no lateral lniotionis imparted to the floating head during its vertical inovementand no angular movement is trans'- mitted Y to` the spindle 19. The adjustable guidevv'ay is positioned in verticalfposition for lapping spur gears since no relative angularmovement is required between the gear and lap since the teeth of the gear and. lap extend in an. axial. direction.

It .villbe apparent that when the linear guide carriedby the annulus 66 is disposed at any angle to the vertical, horizontal move ment Will be imparted .to the slide 7 2 which the pitch cylinder ofthe pinion 80 is equal.

nto the horizontal linear speed of the slide 7 2. During the reciprocating vandY oscillatilllgf:` .movements Vof the spindle 19 any point mom y ing with the spindle .and lying in thepitchv cylinder of the' pinion 80 will describe a helix* about theaxis Vof the spindle, the an o owhich is` equal to the angle at which't eV klinear guide on therannulus 66 is disposed:l withY respect v With the spindle 19V and disposed Within the` to the vertical. Points moving pitch cylinder of thepinion 80 describea.

helix Vof smaller angle than the helix described byfa point on the pitch cylinder of the pinion.. 80 and points outwardly ofthe pitch cylinder so of thepnion 8O will describe helices ofi a greater angle. Ifthe pitch diameter of the gear being lapped is equal to. the pitch diameter ofthe pinion 80, the -annulus 66 'will-be,

adjusted to any angleto the' vertical cornel spending tothe helix'angle of the gear. If

the gear beinglapped is of a different diameter, the anglelat which the linear guide the annulus should be set to' produce` ther required relativerotational movements between the gear and lap is the' angle'whose tangent is equalto-the tangent of the helix angle of the gear times the pitch diameter of the: pinion 80 divided by the pitch diameter of the gear. By employing a lpinion of adiameter less than the gears tobe lapped the amount of angular adjustment of the annulus 66 ina-y be muchv less than the helix angle of sol the'gear, softhatrgearsof high helix angles or worms may lapped Awithout disposing4 the linear guideon the annulus 66 at such high'angles to the vertical as to introduce objeetionably' higlr rictional resistance yto lateral movements of the floating head.4

Accessilnay be obtained to the adjustable annulus 66 for-fixing the same in various j listing the same vertically ,on the posts 5 9 by meansvof a door 8 3 inthe front wall of the housing 22; l v

' In the `operation `of the machine, the. lap- 1 andqgear 2` are mounted on the spindle `19 and arbor 5, as shown in Fig. 1,. and thev annulus 66 is adjusted to bring the linearv Way thereof to they proper angle Withxrespect to the vertical to cause points on the tooth facesfof the lap to move in'helieal pathsy corresponding to helices of the gear tooth faces.l so that ain invariable angular relationship kismaintained between gear tooth faces and' lap' toothE faces during reciprocation. of the lapa`I LAs long as gears having `the same lead areV being lapped?, the adjustment of the annulus erator adjusts the annu'lus` 66 tol the angular positionat which relative reciprocating` and -oscillating movements ofthe gear and. lapfv are properly correlated.

Helical gears orf worms of any helix.v angle las positions of angular adjustment and for ad fwtween said supports and having portionsv may thus be operated upon without changmechanism, the only change in the set-up ot' the angular adjustment of the guideway controlling the lateral movements of the ioating head.

Furthermore, it is vto be understood that 'fthe particular form of apparatus shown and described, and the particular'procedure set forth, are presented for purposes of explanation and illustration, and that various modiications of said apparatus and procedure can be made without departing from my invention as delined in the appended claims. What I claim is: 1. A motion transmitting device comprising a frame having a pair of supports mounted thereon which are provided with opposed guideways, said supports being mounted torV relative reciprocation, one of said supports being mounted for adjustment angularly.

about an axis perpendicular to the plane of its guideway, a floating head interposed between said supports and having portions slidable in said guideways, a member rotatably mounted in one of said supports, and means interposed between said floating head and rotatably mounted member for oscillatf ing the latter.

' 2. A motion transmitting device comprising a frame having apair of supports mounted thereon which are provided with opposed Y guideways, said supports being mounted for relative reciprocation, one of said supports being mounted for adjustment angularly about an axis perpendicular to the plane ot' its guideway, a floating head interposed beslidable in said guideways, a spindle rotatably mounted in one of said supports, and afdriving connection between said spindle and head for oscillating said spindle with a speed ot angular movement proportional to the linear speed of the head along the guideway of the support in which the spindle is mounted.

3. A motion transmitting device comprising a frame having a pair of supports mounted thereon which are provided with opposed guideways, said supports being mounted for relative reciprocaticn, one of said supports being mounted for adjustment angularly about an axis perpendicular to the plane of its guideway, a floating head interposed between said supports and having portions slidable in said guideways, a spindle rotatably mounted in one of said supports and extending at right angles to the guideway of its support, and means interposed between said head and'said spindle for imparting- 4.' A motion transmitting device comprising a frame having a pair of s upports mountr` ed thereon which are'provided with opposed the machine, aside from the interchanging A lof the lap and the indexing change gear, being guideways, said supports being mounted for relative reciprocation, one of said supports being mounted for adjustment angularly about an axis perpendicular to the plane of ed thereon which are provided with opposed guideways disposed in parallel planes, said supports being mounted for relative reciprocation paral lel to the planes of said guideways, one of said supports being mounted for adjustment angularly about an axis perpendicular to the planes of said guideways,

a floating head interposed between said supports and comprising a pair of slides fitting in said guideways and connected together for relative rotation about an axis perpendicular to the planes of the guideways, a rotatably mounted member carried by one of said supports, and means interposed between the rotatably mounted member and the slide on the same support for oscillating said rotatably'mounted member with a speed of angular movement proportional the speed of the actuating slide along its guideway.

6. A motion transmitting device comprisinga frame having a support mounted for reciprocation thereon, a spindle rotatably mounted in said support, a guideway on said support extending at right angles to the spindle, a second support on said said frame having a guideway opposed to the lirst mentioned guideway and disposed in a plane parallel thereto, said second support being angularly adjustable about an axis perpendicular to its guideway, a ioating head interposed between said supports 'and having portions slidable in said guideways, and a driving connection between said head and spindle for oscillating said spindle as said head is reciprocated in the guideway on the spindle support. Y'

7. A lmotion transmitting device comprising a frame having a support mounted for reciprocation thereon, said support having a linear guideway, a second support having a linear guideway thereon, said second support being angularly adjustable about an axis perpendicular to the plane of its guideway to adjust said guideway to different angles with respect to the guideway of the first support, a floating head comprising interconnected relatively movable slides mountedV in said gudewaysrsplldle, and a driving connection between one ol said slides and said pindle for oscillating the spindle as the slide s reeiprocated in vits guideWay.

8. A motion transmitting device eompris ing a frame having a supportin the form of a housing mounted for linear reciprocation on tlie frame, a spindlejournalled in said housing, guides for said liousingcarried by Y the trame and extending into the housing, a guideway carried by the housing and extend'- ing at right angles to said spindle, a second support attache-,dito said guides Within tlie housing, said second support having a guide- Way opposed to tlie irst mentioned guideway and being adjustable about an axis perpendicular to the plane of its guidevvay, a floati ing liead interposed between and supported by said guideways, said head having pivotally connected slides mounted in said guide- Ways, and a driving connection between the slide in the iirst mentioned guidevvay and said spindle for oscillating the spindle as the slide is reciprocated.

9. A motion transmitting device comprising a supporting frame, a support mounted for linear reciproca-tion on the frame, a spindle carried by said support and having l its axis disposed parallel to the line of movement of said support, a guideway on said 80 support extending transversely of said Y spindle, a slide mounted 'to travel in said guidervay., movement imparting means for moving` said slide in its guideway at a speed proportional to the speed of linear movement of the support, means for adjusting said movement imparting means to vary the ratio between the linear speeds of tlie support and slide, and means interposed between the slide and spindle for imparting` to the spindle turn- 40 ing' movements at speeds proportional to the speeds of movement of the slide.

l0. A motion transmitting device comprising a supporting frame, a support mounted for linear reeiprocation on the frame, a spindle carried by said support, a guidevvay on said supportextending transversely of the direction of movement of the support, a slide mounted to travel in said guidevvay, an annulus mounted on the frame independently of said support and having a guidevvay opposed to the guideway on said support, said annulus being adjustable about its axis to vary the of its guideway, a member attached to said slide and engaging in the last mentioned guidervay, and driving means interposed beteween said slide and said spindle to turn the spindle at a rate proportional to tlie linear speed of said slide.

ln testimony whereof l aiix my signature.

so JAMES HOWARD WILLIAMS.vr

lib 

